Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
  • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
  • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/07—Details of compressors or related parts
  • F25B2400/075—Details of compressors or related parts with parallel compressors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/16—Receivers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B30/00—Heat pumps
  • F25B30/02—Heat pumps of the compression type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B40/00—Subcoolers, desuperheaters or superheaters
  • F25B40/02—Subcoolers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B40/00—Subcoolers, desuperheaters or superheaters
  • F25B40/04—Desuperheaters
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
  • Y02A40/00—Adaptation technologies in agriculture, forestry, livestock or agroalimentary production
  • Y02A40/90—Adaptation technologies in agriculture, forestry, livestock or agroalimentary production in food processing or handling, e.g. food conservation
  • Y02A40/963—Off-grid food refrigeration

Definitions

• the invention relates to a reversible recovery system by taking and transferring heat energy between at least two different environments, for example between the outside and a place of life, work, storage or any other requiring a contribution of calories or frigories.
• the heat requirements in cold periods of a place of life, work or other place can be summed up in a simple way in an amount of calories devoted to heating the air and another less significant amount of calories devoted to heating the sanitary water.
• the latter varies greatly depending on the number of people drawing domestic hot water or indirectly generating such a need.
• the energy devoted to heating disappears while the quantity of heat energy devoted to domestic water decreases only to a lesser extent.
• the heating network integrated in the floors of the underfloor heating systems is currently used to produce cooling air conditioning in summer.
• Heat pumps and energy recovery units are characterized by an index called coefficient of performance involved in the energy efficiency of the installation and therefore on the gains made by sourcing part of it from a calorie drawing medium Free.
• the present invention aims to further improve the overall efficiency of heat energy recovery installations using a heat pump.
• the calories are extracted from the rooms and premises.
• the calories are no longer rejected outside but used for other needs, for example the heating of sanitary water, the water of a swimming pool or any other need for heating and even for cooking.
• the heat recovery and transfer system according to the invention having a refrigeration circuit of the heat pump type and several use circuits is characterized in that it consists of a reversible exchanger placed in an external environment, at least one compressor but preferably two compressors including a main compressor and at least a secondary compressor, the latter being used in conjunction with the main compressor, a primary refrigerant circuit formed by a main exchanger for heating the sanitary water, of at least one reversible exchanger for supplying or extracting calories from rooms or premises via a refrigerant, the assembly being closed on the external reversible exchanger by an expansion block and of seperation.
• the circuit according to the invention has high performance and in particular an excellent performance.
• the plurality of calibrated and remotely controlled valves ensure exceptional operating flexibility in both winter and summer modes.
• Figure 1 is the basic diagram of the system according to
• Figure 1 • invention
• Figure 2 is the basic diagram of the invention in the so-called winter configuration, that is to say of consumption of heat energy in heating and domestic hot water
• Figure 3 is the basic diagram in its so-called summer configuration, that is to say when the heating circuit of rooms and premises operates in cooling mode;
• Figure 4 is the basic diagram of a simplified system for small installations in its so-called winter configuration; .
• Figure 5 is the basic diagram of a simplified system for small installations in its so-called summer configuration; .
• FIG. 6 is the basic diagram of a simplified system with a single compressor in its so-called winter configuration; .
• FIG. 7 is the basic diagram of a simplified system with a single compressor in its so-called summer configuration.
• the recovery system has a refrigeration circuit formed by a reversible air exchanger EA traversed by an air flow sent by a fan of exchanger VE then followed by various components including a calibrated valve VC1 controlled remotely, a phase separator S, of a main compressor CP mounted in parallel alone or with at least one secondary compressor CS used in connection with this main compressor CP.
• the main compressor CP supplies a non-reversible primary exchanger EP for desuperheating with condensation partial or total for the transfer of all or part of the calories to a DHW domestic water heating circuit.
• the only one or the main compressor CP is of such size and characteristics that for a given installation it is not overpowered in summer knowing that in winter the complement can be provided by another source of energy or be provided by the or the CS secondary compressors.
• the outputs of the compressors CP and CS are connected at a common downstream point AV of the primary exchanger EP from which develop several branches corresponding to several circuits of use in heating mode or in cooling mode. This connection is made at this level in order to deflect the flow of the secondary compressor (s) CS so as not to lose energy in the form of a pressure drop generated by EP which would be crossed by a gas flow which is too large and unnecessary for this purpose. point.
• Three branches have been shown to illustrate three possibilities of use, for example for the first, use in heating mode by non-reversible terminal units, for example radiators, swimming pool, fan coil units, air heaters, for the second use in heating / cooling by reversible terminal units using hot or cold water, for example: heated floors, fan coil units, air heaters, and for the third use identical to the second.
• non-reversible terminal units for example radiators, swimming pool, fan coil units, air heaters
• hot or cold water for example: heated floors, fan coil units, air heaters
• the first branch consists of a direct connection to a secondary, non-reversible ESI exchanger with return as shown in a BDS expansion and separation block by L1 through a calibrated valve VC2 controlled remotely.
• the operating circuit connected to the secondary output of this ESI exchanger is activated by a PI circulator placed on the hot water circuit.
• the second branch is made up in parallel on the one hand of a valve C4 followed by a calibrated valve VC3 controlled remotely coming from the common point AV and on the other hand of another calibrated valve VC4 'controlled remotely coming from the exit from VC1 and leading to the entry of a reversible exchanger ES2.
• the output of ES2 is connected by L2 to the BDS expansion and separation block.
• the secondary circuit of ES2 is activated by a pump P2 mounted in the hot water circuit.
• the third branch leads to the entry of another reversible secondary exchanger ES3 from two calibrated remote-controlled valves, one VC5 coming from VC1 and the other VC6 coming from the common point AV.
• An auxiliary branch formed by a calibrated VC7 bypass valve, remotely controlled and followed by a valve C5 is mounted in bypass between AV and the output of ES3. This is connected by L3 to the BDS expansion and separation block.
• the ES3 usage circuit is activated by a P3 pump mounted in the usage circuit.
• a calibrated VC8 reversing valve remotely mounted between the air exchanger EA and the EP and ESI exchangers allows the supply of heat in summer mode of the EP and ESI exchangers or the defrosting in winter mode of the EA exchanger.
• Remote-controlled calibrated VCn valves are, for example, of the solenoid type. Because of their multiplicity, one can choose the heat exchanger ESn to supply which corresponds to the circuit in demand and thus benefit from exceptional flexibility and optimization of operation providing additional savings.
• the reversible heat exchanger ES2 can operate in cooling mode while ES3 is in heating mode and ESI is stopped. This is only an example because the combinations are multiple.
• the domestic hot water circuit DHW it conventionally consists of a BEC hot water tank into which a heating circuit is supplied, formed by a circulator P4 and a thermostatic valve VTA controlled in operation by a temperature CAP sensor placed at the outlet of EP.
• the cold water inlet and the hot water outlet of the BEC tank are referenced Gl and G2 respectively.
• the diagrams of FIGS. 1, 2 and 3 end in their upper part with the expansion and separation block BDS to which the lines L1, L2 and L3 of the branches containing the exchangers ESI, ES2 and ES3 terminate and from which three links leave or arrive.
• L4, L5, L6 respectively with first the compressors CP and CS, then with the inlet and the outlet of the reversible air exchanger EA.
• the BDS expansion and separation block consists of the phase separator S, three thermostatic expansion valves with external equalization Dl, D2 and D3.
• D3 is also an electrically controlled regulator. For the first two Dl and D2 they are regulators in summer mode respectively and for the last D3 a regulator in winter or mixed mode. Each regulator is derived by a non-return valve respectively Cl, C2 and C3.
• the regulator Dl derived by its valve Cl is placed in series on the outlet by L2 of one exchanger ES2. As shown, the output of the regulator D1 is connected to D2, to S and to VC2 and therefore to ESI by L1.
• the output of ES3 arrives via line L3 at the inlet of the regulator D2 and the non-return valve C2 connected by its other end to the phase separation unit S.
• the inlet of the regulator D2 is connected to Cl to the inlet of Dl and to S.
• the regulators Dl, D2 and D3 are thermostatic regulators. They are regulated by the temperature measured at the level of their bulbs respectively Bl, B2 and B3, for example mounted as shown, applied to the conduits of the refrigeration circuit in which the refrigerant circulates. These bulbs reflect the temperature of the refrigerant at the point where they are mounted.
• the D3 regulator is a special thermostatic regulator. On its bulb B3 is mounted a resistance R from 10 to 50 Watts energized by an adjustable thermostat ThR placed between CP and EP. It is intended to heat the bulb B3 to cause the larger opening of the regulator D3.
• the explanation of the operation of the heat energy recovery system according to the invention requires two specific descriptive developments, one for each of its two main operating modes, namely: the heating mode only (winter mode), the mixed mode without heating but with cooling (summer mode).
• the operating principle is identical for various powers and independent of the number of exchangers, compressors or the nature or extent of the external recovery or evacuation medium and the supply medium.
• the operating principle is particularly valid in the case of a single compressor.
• the winter regime involves heating rooms and premises and domestic water.
• a refrigerant is used as the vehicle, a first change of state allows to take away a mass of calories taken from an exporting medium to be transferred to a receiving medium by use circuits from the exchangers with this refrigerant.
• the winter regime corresponds to the following constant states:
• the BEC hot water tank is crossed by heating water with limitation of the partial condensation in EP by VTA. . at least one of the exchangers ESI, ES2, ES3 is working.
• the main compressor CP will be put into operation at the same time as the circulator P4 for heating the domestic water.
• one or more secondary compressors CS are called in as needed or an external source of calories.
• CP, P4 and VE are in operation.
• the VC7 calibrated valve is only open if EP is the only exchanger in operation.
• VTA will maintain the temperature of the BEC tank heating water at a minimum value of 45 ° C, for example.
• the bulb or CAP sensor of this VTA valve is placed on the EP primary outlet pipe to optimize the desuperheater function of this exchanger traversed by the high pressure gas flow coming only from the CP compressor.
• VC1 is open to allow recovery of calories from EA via lines L5, L4.
• the other exchangers may be in demand for calories.
• ES1 from EP is crossed by the high pressure gas flow compressed by CP and possibly
• CS. ESI receives a gas flow more or less desuperheated or partially condensed depending on the calorie demand at the secondary level of EP, that is to say the calorie demand of the primary heating circuit of domestic water containing VTA and P4. If the heat exchanger ES2 is in demand for calories, CP, P2 and VE are in operation, and VC3 is open so that ES2 receives the compressed gaseous refrigerant and ensures the supply of calories.
• the EP exchanger desuperheats the high pressure gas flow, or even generates a partial condensation of the flow depending on the demand regulation by VTA.
• VC1 is open to allow the intake of calories from EA.
• the main exchanger EP is traversed by the high pressure refrigerant gas flow which it overheats or even partially condenses as a function of caloric requirements.
• VC7 is systematically closed if one of the ESI, ES2, or ES3 exchangers is in demand for calories. If the temperature of the gaseous refrigerant exceeds for example 90 ° C at the point NI, - the electrical resistance R of additional excitation of the bulb B3 with a power of 10 to 50 W will be energized by an actuated control circuit by an adjustable thermostat ThR placed in NI.
• This function is to maintain the operation of the compressors over a reasonable temperature range over which the performance is optimal. Heating the bulb B3 will cause the expansion valve D3 to open further, which will cause the temperature of the gaseous refrigerant to drop to the level of NI in order to keep the installation within the limits of normal operation.
• This function is innovative because it allows to keep a low overheating at the NI level even in the case of increased compression by a low outside temperature and a high demand for calories by the hot water circuit and this with an identical setting of the regulator.
• phase separator S as used here is a component specially constructed for this assembly. It fulfills the following four main functions:
• This overheating defined as the temperature difference between N4 and N5 se . ra set to the lowest possible value by appropriate adjustment of the holder control. For example, we are targeting an overheating of 10 ° C.
• phase separator S in the refrigerant circuit, the presence of which constitutes at the same time an anti-water hammer bottle, a heat exchanger between the high pressure liquid and the gas at low pressure to increase the efficiency of l 1 reversible EA heat exchanger, protection for CP and CS compressors and a dual-flow liquid tank.
• This phase separator S is with a dip tube in a reserve of liquid fluid.
• the section of its dip tube is larger than the inlet duct to optimize the heat exchanges and allow one evaporation of the last drops of refrigerant contained in the low pressure gaseous fluid.
• the summer regime uses the reversible nature of the system because it is necessary in this climatic period to refresh the rooms and premises.
• the system is mixed because the heating of the domestic water remains as well as possibly totally or partially that of the swimming pool water. It is characterized by:
• ESI, ES2 and ES3 are not crossed by the refrigerant, either because the flow is bypassed, or because the valve in series on the input circuit is closed.
• the circulator P4 of the heating circuit starts operating as well as the main compressor CP.
• the ventilator VE of the air exchanger EA starts at the same time as CP.
• CP discharges the refrigerant in the state of hot gas and under high pressure, for example 20 bars - i.e. 70 ° C.
• the refrigerant liquefies and the heat of condensation is also recovered.
• the liquid then passes through the regulator D3 from which it emerges in the liquid + vapor phase to enter the exchanger EA where it is evaporated.
• the heating circuit regulation loop comprising VTA and P4 makes it possible to establish a level of desuperheating and condensation in EP as a function of the average of the requirement.
• Regulation by R from ThR also plays its role in limiting the temperature of the gaseous refrigerant at the outlet of the compressor CP.
• ESI non-reversible exchanger to heat water for another use for example that of the swimming pool,.
• ES2 and / or ES3 reversible exchangers for cooling rooms and premises.
• CP is in operation and the valves VC8 and VC4 are open.
• the flow of gaseous and high pressure refrigerant passes through EP where a desuperheating and possibly partial or total condensation occur if the domestic water is at a temperature below the set temperature inside the BEC tank, then the flow crosses EA via VC8.
• VE will only be in operation if the temperature measured in N2 is higher than a predetermined temperature, for example 65 ° C. In this case, the calorie requirements at the level of EP and / or ESI are zero.
• CS3 is in demand for frigories
• CP is in operation and the valves VC8 and VC5 are open.
• the flow of high pressure gaseous refrigerant passes through EP where desuperheating and possibly partial or total condensation occurs.
• VE will only be in operation if the temperature measured at N2 indicates a temperature higher than the predetermined value chosen. In this case, the calorie requirements at the level of EP and / or ESI are zero.
• VC5 to be aspirated by CP after passing through S.
• ESI recovers the heat energy from the system if the VC2 valve is open. The latter is only open if the thermostat controlling it is requesting calories.
• ESI will recover the remaining calories from the flow leaving EP in the event that ESI is in demand for calories, the valve VC8 then being closed and VE not controlled in operation.
• the water in the floor circuit is at least 18 ° C and in the primary of ES2 or ES3 the evaporation temperature is around 12 ° C.
• the system is particularly economical because the calories extracted in rooms and premises are only partially discharged outside by EA, the difference being used for water heating needs sanitary or pool water.
• the EA air exchanger used as an evaporator in winter mode can frost, i.e. cover itself with a layer of ice. Since the ice is a good thermal insulator, the ice shell constitutes a serious handicap for the proper functioning of the heat exchanger. It is therefore necessary to defrost as soon as the ice covers the external structures of the external exchanger EA.
• the compressor CP is cut, all the valves are closed and the VE fan is switched off.
• VC8 reversing valve is opened for a short time (approximately one minute).
• a complete defrost cycle lasts no more than three minutes and no more than three defrosts are necessary even in very cold weather.
• FIGS. 4 and 5 relate to a simplified variant for a small installation, for example that provided for a small single-family dwelling of the pavilion type. It includes the essential elements and components, namely:. the reversible EA air exchanger with the medium outside and its VE fan,
• a non-reversible main EP exchanger for transferring calories to a circuit for use in heating domestic hot water ECS in a BEC tank with temperature probe STh by a circuit containing a circulator P4 and a thermostatic valve VTA controlled by a sensor CAP placed at the outlet of the EP exchanger,
• a BDS expansion and separation block comprising a phase separator S and two thermostatic expansion valves Dl and D3 with heat-sensitive bulbs Bl and B3 derived by non-return valves Cl and C3, one of which is Dl in inversion regime and the other winter D3 in heating,. the following calibrated valves:
• VC1 main valve .
• VC5 return valve .
• VC6 heating exchanger valve .
• VC7 bypass valve .
• the EA exchanger operates as an evaporator, the compressor (s) CP, CS receives (fri) t the refrigerant evaporated through VC1, it passes through the phase separator S and is compressed, for example at 20 bars, or 70 ° C, by CP with possibly the help of CS. It then crosses the primary of the EP exchanger where it
• the partially superheated and condensed fluid will continue to condense in the primary of the reversible exchanger ES3 passing through VC6 in order to transfer the rest of the calories - which it transports in a heating use circuit, for example via a P3 circulator.
• the condensed refrigerant then crosses the phase separator S of the expansion and separation block BDS passing through Cl, to relax in D3 and return to the liquid and expanded state in the air exchanger EA where it evaporates in taking away the amount of heat corresponding to its dimensional and operating characteristics.
• the refrigerant in gaseous state arrives at the inlet of the compressors by VC1 and circulates in the circuit as previously indicated.
• the bulb B3 of D3 can be heated by a resistor R of low power from the temperature values of the refrigerating fluid at the outlet of the main compressor CP, thus transforming it into a thermostatic expansion valve with external equalization for a temperature of the refrigerating fluid at the CP output which exceeds a predetermined threshold, for example 90 ° C.
• Summer operation In summer operation mode (figure 5), the production of hot water and the regulation of its heating circuit are carried out in the same way as previously.
• the evaporated fluid comes from the output of the reversible exchanger ES3 through VC5 and supplies the only compressor CP in operation. Indeed, the cooling function of rooms and premises involves the passage of calories from the secondary of the ES3 exchanger to its primary and thus its transfer in the refrigeration circuit.
• This ES3 exchanger operating as an evaporator, takes the calories from the refrigerant leaving the gas to be compressed in CP and used for heating domestic water.
• the system can operate in a short circuit when the calorie demand of the domestic hot water circuit DHW is high, that is to say without using the external exchanger EA for heat generation. Under these conditions, all the calories recovered by ES3 are used and it proves useless to evacuate them outside by EA.
• the operating conditions are such that the refrigerant is condensed entirely in the primary of EP from which it emerges in the liquid state, crosses VC6, arrives liquid at the inlet of the primary of ES3 and crosses S, where it evaporates and returns to the inlet of the CP compressor.
• the refrigerant passes through the phase separator S before entering the primary of ES3, in order to purify it from any gas bubbles.
• This simplified implementation corresponds well to the needs of a single-family dwelling of the pavilion type.
• the operation is also almost identical. It differs only in the absence of a secondary compressor CS.

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• 2000
  • 2000-11-10 FR FR0014477A patent/FR2816697B1/fr not_active Expired - Fee Related
• 2001
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  • 2001-11-09 WO PCT/FR2001/003504 patent/WO2002039033A1/fr active IP Right Grant
  • 2001-11-09 EP EP01993799A patent/EP1337793B1/de not_active Expired - Lifetime
  • 2001-11-09 AU AU2002223048A patent/AU2002223048A1/en not_active Abandoned
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  • 2001-11-09 AT AT01993799T patent/ATE364161T1/de not_active IP Right Cessation
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• 2007
  • 2007-09-04 CY CY20071101146T patent/CY1106844T1/el unknown

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